Turbo compressor

ABSTRACT

The present invention relates to a turbo compressor which is capable of minimizing deformation of construction parts occurred in welding or after welding and simplifying manufacture and assembly by forming the outer diameter of a driving shaft so as to be stepped and combining the construction parts with bolts and pins. The turbo compressor in accordance with the present invention comprises a sealed container having inlets separately on both sides, a first bearing housing and a second bearing housing and a driving motor installed inside of the sealed container, a driving shaft its both ends separately inserted-penetrates through holes of the first and second bearing housings, a sealing member fixedly combined to the first bearing housing, a radial supporting mean for supporting the driving shaft to radial direction, a first and a second impellers and a first and a second diffuser members fixedly combined to the both ends of the driving shaft, an interconnection pipe for connecting the inlets, and an axial supporting mean for supporting the driving shaft to axial direction.

BACKGROUND OF THE INVENTION

[0001] 1. Field of the Invention

[0002] The present invention relates to a turbo compressor, in particular to a turbo compressor which is capable of minimizing deformation of construction parts occurred in welding or after welding, and simplifying a manufacture and an assembly.

[0003] 2. Description of the Prior Art

[0004] In general, a refrigerating cycle apparatus comprises a compressor for compressing working fluid such as a refrigerant in order to convert it into a high temperature and high pressure state, a condenser for releasing internal latent heat to outside while converting the high temperature and high pressure state working fluid compressed on the compressor into liquid phase state, an expanding unit for lowering pressure of the working fluid converted into the liquid phase on the condenser, and a vaporizer for absorbing heat of the outside while vaporizing the liquid phase state working fluid expanded on the expanding unit, and the each construction part is connected by an interconnection pipe.

[0005] As described above, the refrigerating cycle apparatus is installed on a refrigerator or an air conditioner in order to preserve foodstuff as a fresh state by using cold air generated from the vaporizer or maintain a room as a pleasant state by using cold air or hot air generated from the vaporizer or condenser.

[0006] Meanwhile, the compressor comprises a power generation unit for generating a power, and a compressing unit for compressing gas in accordance with a driving force transmitted from the power generation unit. The compressor is divided into a rotary compressor, a reciprocating compressor, a scroll compressor, etc. in accordance with a gas compressing method of the compressing unit.

[0007] In more detail, in the rotary compressor, a rotating shaft is rotated by being transmitted the rotating driving force of a motor unit, an eccentric portion of the rotating shaft is rotated by being line-contacted with an inner surface of a cylinder, accordingly the gas is compressed while changing volume of the internal of the cylinder.

[0008] And, the reciprocating compressor compresses the gas by being transmitted the rotating driving force of the motor unit as a linear reciprocation motion to a piston through a crank shaft and a connecting road and performing the linear reciprocation motion of the piston inside of the cylinder.

[0009] In addition, the scroll compressor compresses gas by being transmitted the rotating driving force of the motor unit, performing a rotating operation of a rotary scroll engaged into a fixed scroll, and changing volume of a compress pocket formed by the wrap of the fixed scroll and the wrap of the rotary scroll.

[0010] However, because the rotary compressor, reciprocating compressor, and scroll compressor absorb gas, compress it, and discharge it by periodic volume change, the compressed gas can not be discharged consecutively, in addition vibration and noise of the apparatus occur due to the periodic discharge of the compressed gas.

[0011] On the contrary, a turbo compressor having an advantage in the vibration and noise is used for a bulk air conditioning such as a building, a factory, a plant, a ship etc. until now, accordingly only a custom small quantity can be produced because of its volume and scale.

[0012] However, there is limit to perform mass production of a small turbo compressor with a structure and a manufacture method of the conventional bulk turbo compressor.

SUMMARY OF THE INVENTION

[0013] The object of the present invention is to provide a turbo compressor which is capable of manufacturing and assembling parts easily.

[0014] In order to achieve the object, the turbo compressor in accordance with the present invention comprises a sealed container having internal space and an inlet separately on both sides, a first bearing housing and a second bearing housing installed left and right portion inside of the internal space of the sealed container with a certain interval and having separately a through hole on each center portion, a driving motor installed between the first bearing housing and second bearing housing, a driving shaft combined to the driving motor and its both ends are separately inserted-penetrated into the through holes of the first bearing housing and second bearing housing, a sealing member for being inserted by the driving shaft and fixedly combined to the first bearing housing, radial supporting means separately inserted between the driving shaft and first bearing housing and between the driving shaft and second bearing housing, a first impeller fixedly combined to the end of the driving shaft, a second impeller fixedly combined to the other end of the driving shaft, a first diffuser member fixedly combined to the sealing member by placing on the outer circumference of the first impeller, a second diffuser member fixedly combined to the second bearing housing by placing on the outer circumference of the second impeller, an interconnection pipe for connecting the inlets, and an axial supporting mean installed between the side of the driving shaft and side of the sealing member.

BRIEF DESCRIPTION OF THE DRAWING

[0015]FIG. 1 is a cross sectional view illustrating a turbo compressor in accordance with the present invention.

[0016]FIG. 2 is a cross sectional view illustrating magnified a first impeller and a first compressor part constructing the turbo compressor in accordance with the present invention.

[0017]FIG. 3 is a cross sectional view illustrating magnified a second impeller and a second compressor part constructing the turbo compressor in accordance with the present invention.

[0018]FIG. 4 is a front view illustrating a radial supporting mean constructing the turbo compressor in accordance with the present invention.

[0019]FIG. 5 is a front view illustrating an axial supporting mean constructing the turbo compressor in accordance with the present invention.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT

[0020] Hereinafter, a turbo compressor in accordance with the present invention will now be described with reference to accompanying drawings.

[0021] As depicted in FIG. 1, in the turbo compressor in accordance with the present invention, a first bearing housing 20 and a second bearing housing 30 are separately installed on the left and right side with a certain interval inside of inner space of a sealed container 10.

[0022] The internal space of the sealed container 10 is divided into a motor chamber M and a first and a second compressing chamber A, B by the first and second bearing housings 20, 30 installation position.

[0023] In more detail, the space between the first and second bearing housings 20, 30 is formed as the motor chamber M, the space between the first bearing housing 20 and the side of the sealed container 10 is formed as the first compressing chamber A, and the space between the second bearing housing 30 and the other side of the sealed container 10 is formed as the second compressing chamber B.

[0024] The sealed container 10 comprises a cylinder body unit 11 having a certain inner diameter and a certain length, and a first and second covered plates 12, 13 formed so as to have dimension corresponding to the radial cross section of the cylinder body unit 11 in order to cover-combine the both ends of the cylinder body unit 11.

[0025] As depicted in FIGS. 2 and 3, the first and second covered plates 12, 13 have a disk shape, inlets F1, F2 are separately formed on the center portion, shroud portions 12 a, 3 a are curved-formed by extending the outer circumference of the inlets F1, F2 as a curved surface similar with a cone shape, and volute portions 12 b, 13 b are separately formed between the outer circumference end of the shroud portions 12 a, 13 a and the both ends of the cylinder body unit 11.

[0026] Herein, the first and second covered plates are combined by the cylinder body unit 11 after press-processing of the first and second covered plate plates 12, 13 and processing of the shroud portions 12 a, 13 a.

[0027] Hereinafter, the installation process for installing the first and second bearing housings 20, 30 having the through holes 21, 31 formed on the center portion inside of the sealed container 10 will now be described.

[0028] When the outer circumference of the first and second bearing housings 20, 30 are separately contacted to the fixing member 40 by inserting-fixing the fixing member 40 between the inner circumference of the sealed container 10 and outer circumference of the first and second bearing housings 20, 30, the first and second bearing housings 20, 30 and fixing member 40 are fixedly combined by a fastening mean 41.

[0029] Generally, a bolt is used as the fastening mean 41.

[0030] Accordingly, the present invention can improve productivity by minimizing deformation in the welding or after welding and reducing welding time by fastening the first and second bearing housings 20, 30 with the bolt without welding it when the first and second bearing housings 20, 30 are assembled.

[0031] Meanwhile, a driving motor 51 comprising a stator 51 fixedly combined to the inner circumference of the sealed container 10 and a rotator 52 inserted inside of the stator 51 so as to be rotatable is installed inside of the motor chamber M.

[0032] In addition, a driving shaft 60 having a certain length is inserted inside of the rotator 52 of the driving motor 50, the both ends of the driving shaft 60 are separately inserted into the through hole 21 of the first bearing housing 20 and through hole 31 of the second bearing housing 30.

[0033] Herein, a bearing bush 70 having a certain shape is inserted between the first bearing housing 20 and driving shaft 60, the bearing bush 70 is inserted-fixed by contacting to the outer circumference of the driving shaft 60, at the same time has a certain interval with the inner circumference of the through hole 21 of the first bearing housing 20.

[0034] Meanwhile, the sealing member 80 having a certain shape is fixedly combined to the first bearing housing 20 in order to insert the driving shaft 60 inside of it and cover the bearing bush 70.

[0035] The shape of the sealing member 80 will now be described in more detail. A labyrinth sealing part 81 having a plurality of consecutive ring shape grooves is formed on the inner circumference of the sealing member 80 where the driving shaft 60 is inserted.

[0036] In addition, the radial supporting means 90, 90 for supporting the driving shaft 60 to the radial direction are separately inserted between the driving shaft 60 and first bearing housing 20 and between the driving shaft 60 and second bearing housing 30.

[0037] As depicted in FIG. 4, the radial supporting mean 90 comprises a plurality of foils S having a sheet shape with a certain dimension.

[0038] Meanwhile, a first impeller 100 is fixedly combined to the end portion of the driving shaft 60, and a second impeller 110 is fixedly combined to the other end portion of the driving shaft 60. Herein, the first impeller 100 is combined so as to place on the first compressing chamber A, and the second impeller 110 is combined so as to place on the second compressing chamber B.

[0039] The first and second impellers 100, 110 are formed so as to be similar to the cone shape, when the first and second impellers 100, 110 are combined to the end portion of the driving shaft 60, they are placed on the portions corresponding to the shroud portions 12 a, 13 a of the first and second covered plates 12, 13.

[0040] In other words, the first impeller 100 and second impeller 110 are combined to the driving shaft 60 as a back to back form.

[0041] And, as depicted in FIG. 2, the first diffuser member 130 is placed on the outer circumference of the impeller 100 and is fixedly combined to the sealing member 80, the first diffuser member 130 performs a function for converting dynamic pressure occurred by the first impeller 100 into constant pressure with the shroud portion 12 of the curved portion of the first covered plate 12 and the volute portions 12 b, 13 b.

[0042] In addition, the second diffuser member 140 placed on the outer circumference of the second impeller 110 is fixedly combined to the second bearing housing 30, the second diffuser member 140 performs a function for converting dynamic pressure occurred by the second impeller 110 into constant pressure with the shroud portion 12 of the curved portion of the first covered plate 12 and the volute portions 12 b, 13 b.

[0043] Meanwhile, the sealing member 80 is combined to the first bearing housing by a pin P2, the first diffuser member 130 is combined to the sealing member 80 by a pin P1, the sealing member 80 and first diffuser member 130 are fixed by adhering and fixing the first covered plate 12 of the sealed container 10 to the cylinder body unit 11.

[0044] In addition, the second diffuser member 140 is combined to the second bearing housing 30 by a pin P3, the second diffuser member 140 is fixed by adhering and fixing the second covered plate 13 of the sealed container 10 to the cylinder body unit 11.

[0045] And, the inlet F2 placed on the side of the first compressing chamber A and the side of the second compressing chamber B is connected by an interconnection pipe 150 for guiding gas one-step-compressed on the first compressing chamber A by the rotation of the first impeller 100 to the second compressing chamber B.

[0046] And, the present invention comprises a gas discharge flow channel for guiding the gas two-step-compressed on the second compressing chamber B by the rotation of the second impeller 110 so as to discharge to the external of the sealed container 10 through the motor chamber M while cooling the driving motor 50.

[0047] In more detail, the gas discharge flow channel comprises a plurality of first through holes 32 formed on the second bearing housing 30 in order to make the gas two-step-compressed on the second compressing chamber B flow into the motor chamber M, a plurality of second through holes 53 formed on the driving motor 50 in order to make the gas flowed into the motor chamber M through the first through hole 32 pass the driving motor 50, and an outlet 11 a formed on the side of the sealed container 10 in order to make the gas cooled the driving motor 50 discharge to the outside of the sealed container 10.

[0048] Herein, it is advisable to form the second through hole 53 on the stator 51 side of the driving motor 50.

[0049] Herein, form of the driving shaft 60 will now be described in more detail. In the driving shaft 60, the outer diameter d1 of the portion placed on the second bearing housing 30 is same or smaller than the outer diameter d2 of the rotator 52, in the bearing bush 70, the outer diameter d3 of the portion placed inside of the first bearing housing 20 is larger than the outer diameter d2 of the rotator 52.

[0050] Accordingly, the outer diameter of the driving shaft 60 is formed so as to be stepped, accordingly the driving shaft 60 can be smoothly inserted into inside of the bearing housings 20, 30.

[0051] Meanwhile, an axial supporting mean 160 for supporting axial direction power affecting on the driving shaft 60 by pressure difference of the first compressing chamber A, motor chamber M, second compressing chamber B is installed between the side surface of the bearing bush 70 and side surface of the sealing member 80.

[0052] As depicted in FIG. 5, the axial supporting mean 160 comprises a plurality of foils S having a sheet shape.

[0053] In more detail, the driving shaft 60 combined to the both ends with the first and second impellers 100, 110 compressing the refrigerant gas while rotating separately on the first and second compressing chambers A, B accepts the power from the one axial direction or both axial directions, but it can rotate in the stable supported state without lean.

[0054] Meanwhile, the inlet F1 placed on the first compressing chamber A is connected to a vaporizer (not shown), the outlet 11 a of the sealed container 10 is connected to a condenser (not shown), the sealed container 10 is fixedly supported by a holder 170 having a certain shape.

[0055] Hereinafter, the operation and effect of the turbo compressor in accordance with the present invention will now be described.

[0056] First, when the power is applied, the rotator 52 is rotated in accordance with the interaction of the stator 51 and rotator 52 of the driving motor 50.

[0057] As described above, when the rotator 52 of the driving motor 50 rotates, the driving shaft 60 combined to the rotator 52 rotates, the driving force of the driving shaft 60 is transmitted to the first and second impellers 100, 110, accordingly the first and second impellers 100, 110 are separately rotated in the first and second compressing chambers A, B.

[0058] When the first and second impellers 100, 110 are rotated, the refrigerant gas passing the vaporizer through the inlet F1 connected to the first compressing chamber A flows into the first compressing chamber A, and is one-step-pressed.

[0059] The refrigerant gas one-step-pressed on the first compressing chamber A flows into the second compressing chamber B through the inlet F2 formed on the second compressing chamber B through the inner connection pipe 150, and is two-step-pressed on the second compressing chamber B.

[0060] The refrigerant gas two-step (again)-pressed on the second compressing chamber B flows into the motor chamber M through the first through hole 32, cools the driving motor 50 while flowing the motor chamber M through the second through hole 53, the refrigerant gas cooled the driving motor 50 is discharged to the condenser side through the outlet 11 a.

[0061] In other words, the refrigerant gas two-step-compressed on the second compressing chamber B is discharged to the condenser side through the gas discharge flow channel.

[0062] Herein, the refrigerant compressing process on the first and second compressing chambers A, B will now be described. The refrigerant gas flowed through the inlets F1, F2 have a kinetic energy, namely, kinetic pressure by getting a centrifugal force while flowing between the each shroud portions 12 a, 13 a and wings of the impellers 100, 110 by the rotating force of the each impellers 100, 110. And, the kinetic energy of the refrigerant gas is converted into constant pressure, namely, pressure energy while passing through the each diffuser member 130, 140 and volute portions 12 b, 13 b continually, accordingly the pressure is heightened.

[0063] Herein, in the refrigerant gas compressing process, because the pressure of the first compressing chamber A is smaller than the pressure of the second pressing chamber B and motor chamber M, the axial force affects on the driving shaft 60.

[0064] The force affected to the axial direction is supported by the plurality of foils as the axial supporting mean 160 for performing the gas bearing function by installed between the sealing member 80 and bearing bush 70.

[0065] Meanwhile, the force affected to the radial of the driving shaft 60 by the driving shaft 60 and parts combined to the driving shaft 60 is supported by the plurality of the foils as the radial supporting mean 90 for performing the gas bearing function between the outer circumference of the driving shaft 60 and the inner circumference of the first and second bearing housings 20, 30.

[0066] In addition, pressure leakage due to the pressure difference between the motor chamber M and first compressing chamber A by the labyrinth sealing part 81 of the sealing member 80 is prevented.

[0067] Accordingly, in the turbo compressor in accordance with the present invention, the gas is consecutively pressed and is discharged while the kinetic energy is converted into the constant pressure by the rotating force of the first and second impellers 100, 110, accordingly vibration noise lowers and compressing performance heightens.

[0068] And, among the parts constructing the compressing chamber, when the parts for fixing the position to the axial are fastened by the pins P1, P2, P3 without using bolt etc., and fixedly combined by the first and second covered plates 12, 13 of the sealed container 10, accordingly the productivity can be improved.

[0069] In addition, the first and second covered plates 12, 13 are produced by a press fabrication, after the press fabrication, the shroud portion 12 a requiring accurate measure is after-processed, accordingly the manufacture cost and manufacture time can be reduced.

[0070] And, because the outer diameter of the driving shaft 60 is formed so as to be stepped, the driving shaft 60 can be smoothly inserted inside of the first and second bearing housings 20, 30.

[0071] In other words, in assembling, after the first and second bearing housings 20, 30 are combined to the sealed container 10, the driving shaft 60 can be inserted into the one direction by reducing diameter of the driving shaft 60 gradually (d3>d2>d1), accordingly the present invention can improve convenience of the assembly and reduce assembly time.

[0072] In addition, the first and second bearing housings 20, 30 are combined when the fixing member 40 is pressed-inserted into the sealed container 10, accordingly the present invention can have simple assembly process by a easier concentric alignment of the first and second bearing housings 20, 30.

[0073] As described above, the turbo compressor in accordance with the present invention can have high compressing performance, can reduce the vibration noise, and can improve the credibility by sucking, compressing, discharging the gas consecutively while the first and second impellers converts the kinetic energy into the constant pressure by rotating in accordance with the driving force of the driving motor. In addition, the turbo compressor in accordance with the present invention can reduce manufacturing cost and can improve the assembly productivity by simplifying the process of the construction parts and assembly process.

[0074] As the present invention may be embodied in several forms without departing from the spirit or essential characteristics thereof, it should also be understood that the above-described embodiments are not limited by any of the details of the foregoing description, unless otherwise specified, but rather should be constructed broadly within its sprit and scope as defined in the appended claims, and therefore all changes and modifications that fall within the meets and bounds of the claims, or equivalence of such meets and bounds are therefore intended to be embraced by the appended claims. 

What is claimed is:
 1. A turbo compressor, comprising: a sealed container having internal space and an inlet separately on both sides; a first bearing housing and a second bearing housing installed left and right portion inside of the internal space of the sealed container with a certain interval and having separately a through hole on each center portion; a driving motor installed between the first bearing housing and second bearing housing; a driving shaft combined to the driving motor and its both ends are separately inserted-penetrated into the through holes of the first bearing housing and second bearing housing; a sealing member for being inserted by the driving shaft and fixedly combined to the first bearing housing; radial supporting means separately inserted between the driving shaft and first bearing housing and between the driving shaft and second bearing housing; a first impeller fixedly combined to the end of the driving shaft; a second impeller fixedly combined to the other end of the driving shaft; a first diffuser member fixedly combined to the sealing member by placing on the outer circumference of the first impeller; a second diffuser member fixedly combined to the second bearing housing by placing on the outer circumference of the second impeller; an interconnection pipe for connecting the inlets; and an axial supporting mean installed between the side of the driving shaft and side of the sealing member.
 2. The turbo compressor according to claim 1, wherein the space between the first bearing housing and sealed container is formed as a first compressing chamber, and the space between the second bearing housing and sealed container is formed as a second compressing chamber.
 3. The turbo compressor according to claim 1, wherein the sealed container comprises: a cylinder body unit having a certain inner diameter and a certain length; and a first covered plate and a second covered plate formed so as to have dimension corresponding to radial cross section of the cylinder body unit in order to cover-combine separately to the both ends of the cylinder body unit.
 4. The turbo compressor according to claim 1, wherein at least one fixing member is inserted-fixed between the inner circumference of the sealed container and the outer circumference of the first and second bearing housings, and the fixing member is combined to the first and second bearing housings by a fastening mean.
 5. The turbo compressor according to claim 4, wherein the fastening mean is a bolt.
 6. The turbo compressor according to claim 1, wherein a bearing bush having a certain shape is inserted between the first bearing housing and driving shaft.
 7. The turbo compressor according to claim 1, wherein the sealing member comprises a labyrinth sealing part on the inner circumference.
 8. The turbo compressor according to claim 1, wherein the radial mean supporting mean comprises a plurality of foils having a sheet shape.
 9. The turbo compressor according to claim 1, wherein the sealing member is combined to the first bearing housing by a pin, and the first diffuser member is combined to the sealing member by a pin.
 10. The turbo compressor according to claim 1, wherein the second diffuser member is combined to the second bearing housing by a pin.
 11. The turbo compressor according to claim 1, wherein a gas discharge flow channel is formed inside of the sealed container.
 12. The turbo compressor according to claim 11, wherein the gas discharge flow channel comprises a plurality of first through holes formed on the second bearing housing, a plurality of second through holes formed on the driving motor, and an outlet formed on the side of the sealed container.
 13. The turbo compressor according to claim 12, wherein the second through hole is formed on a stator of the driving motor.
 14. The turbo compressor according to claim 1, wherein the outer diameter of the driving shaft portion placed on the second bearing housing is same or smaller than the outer diameter of a rotator, and the outer diameter of the bearing bush portion placed inside of the first bearing housing is bigger than the outer diameter of the rotator.
 15. The turbo compressor according to claim 1, wherein the axial supporting mean comprises a plurality of foils having a sheet shape. 